Knitting machines



5 Sheets-Sheet l Filed Sept.

INVENTOR. JOHN A. CURRIER ATTORNEYS Feb. 28, 1967 J. A. CURRIER KNITTING MACHINES 3 Sheets$heet 2 Filed Sept. 9, 1963 FIG. 4.

FIG. 5.

FIG. 2.

INVENTOR. JOHN A. CURRIER ATTORNEXIS 1967 J. A. CURRIER 3,306,079

KNITTING MACHINES Filed Sept. 9, 1963 5 Sheets-Sheet 5 Fl 6. 7i

INVENTOR JOHN A.CURRER United States Patent 3,306,079 KNITTING MACHINES John A. Currier, Gilford, N.H., assignor to Scott & Williams, Incorporated, Laconia, N.H., a corporation of Massachusetts Filed Sept. 9, 1963, Ser. No. 387,561 29 Claims. (Cl. 66-134) This invention relates to knitting machines and particularly to circular knitting machines provided with transfer dials and the operations of such machines.

Particularly in the case of circular knitting machines for the production of ladies hoisery, transfer dials are provided for the formation of turned Welts. Courses initially formed on the needles are transferred to elements in such a dial and held during the knitting of a welt, the transferred courses being then retransferred to the needles preparatory to the continued knitting of the leg and other portions of a stocking.

Heretofore such a dial has been driven in 1:1 relationship with the needle cylinder (or has been stationary with a stationary needle cylinder) because of the necessity involved for maintaining straight wales and definite relationship between the needles and transfer elements during the transfer operations.

However, as exemplified below, it is sometimes desirable to provide a differential speed between the dial and cylinder. One of the objects of the present invention is to provide a driving arrangement by which at different times both differential speeds and the same speed may be provided to a cylinder and dial.

While the invention may be applied for other purposes, a particular use thereof is in the achievement of short cut ends of a splicing yarn during a splicing operation.

In the past splicing was carried out above the heel and/ or in the foot of a stocking by continuous knitting of a main yarn with the introduction of a splicing yarn to predetermined panels of needles at the rear of the ankle and/or at the sole of the foot. As originally carried out this splicing involved floating of the splicing yarn from the end of each partial course in which it was incorporated to the beginning of the next such partial course, and completion of a stocking involved the cutting out of the floats. Recently, however, splicing has been accomplished by severing the splicing yarn at both end of each spliced course, i.e. at the time of its introduction to the needles and at the time of its removal therefrom. This procedure if it involved mere cutting of the spliced yarn by old types of cutting devices would leave objectionable ends free within the stocking; but by the use of so-called short end clippers relatively short yarn ends would be left within the stocking so as not to be particularly objectionable. However, even through the use of such cutters or clippers, a problem has arisen involving the production of unduly long yarn ends at the ends of the partial spliced courses.

This has been due to the fact that the yarns at the time of cutting when introduced and removed necessarily occupy rather different paths with respect to the machine elements. While the problem involved will become clearer hereafter in discussing operations, it may be briefly stated that when a yarn is introduced to a panel of needles involved in splicing it may be engaged by a member rotating with the transfer dial at a point closely adjacent to and above the first needle to seize the yarn so that as it is carried around to a point of severance it extends substantially vertically upwards from the first needle to engage it so that it is well presented to a cutter in a fashion to produce a short yarn end. But when it is removed from action, there is a delay, in efiect, in its engagement with the element associated with the dial so that as it is carried around to the cutting position it extends upwardly diagonally. The result is that cutting is effected at a substantially greater distance from the needle which knits it last, thus producing an objectionably long yarn end.

It is a further object of the present invention to prevent this objectionable type of operation, and the solution of the problem involves having the yarn-engaging element associated with the dial and moving therewith advanced faster than the needle cylinder so that the diagonal path of the yarn is raised to be more nearly vertical at the time of severance.

The foregoing and other objects of the invention particularly relating to details of construction and operation will become more apparent from the following description, read in conjunction with the accompanying drawings, in which:

FIGURE 1 is a vertical section taken through the upper portion of a knitting machine provided in accordance with the invention and showing particularly in association with a needle cylinder a dial and its driving connections which provide for the same rotational speed of the needle and dial and differential speeds thereof;

FIGURE 2 is a plan view of the dial cap and elements associated therewith together with yarn feeding means and a trimmer or cutter;

FIGURE 3 is a horizontal sectional view on the plane 3-3 in FIGURE 1 looking downwardly at one of a pair of associated gears shown in FIGURE 1;

FIGURE 4 is a similar sectional view on the plane 4-4 in FIGURE 1 looking upwardly at the other of the associated gears;

FIGURE 5 is a vertical section taken on the plane indicated at 5-5 in FIGURES 3 and 4;

FIGURE 6 .is a fragmentary diagrammatic view showing needles, sinkers, and associated yarn engaging element and a trimming blade, the diagram illustrating the cutting of yarn at the beginning of a spliced partial course; and

FIGURE 7 is a view similar to FIGURE 6 but showing the operation of cutting a yarn at the end of the formation of a spliced partial course.

Only so much of a knitting machine is illustrated as is involved directly in the matter of the invention. It will be understood that the knitting machine contains the conventional elements involved in the formation of stockings with turned welts, and since the other elements are wellknown they need not be illustrated. The machine shown is of the rotating cylinder type involving the needle cylinder 2 provided with the usual axial slots for the independently movable latch needles 4 which are controlled in completely conventional fashion by means of the usual cams and other elements. Such other elements may include pattern jacks, intermediate jacks, pickers, etc., all conventional. Conventional sinkers 6 provided with nebs and the usual platforms 8 over which stitches are drawn are radially slidable in the sinker dial 10 and are provided with the usual butts controlled by cams in the sinker cap 12 which is mounted for the usual limited oscillatory movements for the purpose of properly controlling sinkers during the reciprocatory knitting of heels and toes. The usual dial 14 mounts the radially slidable transfer elements 16, the movements of these being controlled in conventional fashion by cams carried by the stationary dial 18 acting on butts of the elements 16. Carried by and secured to the dial above the ends of the elements 16 there is the annular ring '20 provided with teeth 22 arranged to engage portions of yarn extending to needles. For the severing or trimming of yarn ends there is provided the cutter 24 of the razor blade type secured in fixed position on a conventional mounting which is not shown. As illustrated in FIGURES 6 and 7, the cutter blade 24 is located as close as possible to the neb portions of the sinkers 6. In these figures the level of the sinker ledges 8 over which stitches are drawn is indicated at 8A. The yarn trimming arrangement is generally similar to that shown in the patent to Stack et al. 2,824,436 and need not be described in detail. It may be remarked, however, that following the drawing of stitches at the yarn feed point the needles are raised to a tuck level and then lowered as indicated in FIGURES 6 and 7 to pass below the cutter blade 24. This permits the cutter blade to be located at the low position just above the sinkers as illustrated.

The machine illustrated is of single feed type, though it will be understood that the invention is equally applicable to multi-feed machines. Illustrated in FIGURE 2 -is the main yarn feeding finger 26 and the splicing yarn feeding finger 28 arranged to feed yarn from the usual throat 30 provided in the latch r-ing assembly. Additional yarn feeding fingers may be provided in the usual fashion to provide heavier reinforcing yarn to form, for example, the welt, heel and toe. The fingers are controlled in usual fashion.

While the splicing yarn may be introduced selectively to needles by a yarn-feeding finger which is moved downwardly into operation and upwardly out of operation during each course in which splicing is to occur, the preferred method of knitting the splicing yarn which will be assumed in the present case is the following:

Needles of the panel on which splicing is to occur are raised to a high cleared height and the other needles are raised to a low cleared height ahead of the feed. The main yarn is fed from a finger 26 which is in action to all of the needles to knit complete courses, but the splicing yarn feeding finger 28 is arranged in advance of the main yarn feeding finger so as to feed yarn only to the needles occupying the high cleared level, so that only these will take and knit the splicing yarn. This insures the introduction of the splicing yarn on a particular needle in each course and its withdrawal from a particular needles in each course, and this occurs without the necessity for vibration of the splicing yarn finger. Pattern mechanism may, of course, control the needles constituting the ends of the splicing panel for the formation of stepped or otherwise varied spliced areas. All of the elements so far described and their basic operations are conventional.

There will now be described the aspects of the novel dial drive involved in accordance with the present invention. A vertical drive shaft 36 is, preferably, driven at the same rotational speed as the needle cylinder and, as shown, in the same counterclockwise direction of rotation during rotary knitting, oscillating with the needle cylinder during reciprocatory knitting. Such a shaft is essentially similar to that conventionally used for driving a dial, the drive being from the conventional cylinder driving mechanism which need not be described. A ratio of drive other than 1:1 with the needle cylinder may be used, with appropriate changes of the gearing as hereafter described, but in the specific arrangement shown the drive is as just mentioned.

Secured in a slot in the upper portion of this shaft is a fixed key 38 the major portion of which is sunk within the circumference of the shaft while a small projection 40 projects radially beyond the shaft. As will shortly appear this projection effects the driving operation.

Journalled on the shaft 36 are a pair of gears 44 and 46 adjacent to each other and having cooperating bearing surfaces at 48. A compression spring 50 reacting between a fixed washer and a washer 52 engaging the lower gear 44 serves to urge the gears upwardly together with a bushing 54 which is also journalled on the shaft 36. Pins 56 carried by the left hand end of a forked lever 58 pivoted at 60 engage openings in the bushing 54 to impart vertical movements thereto. The lever 58 has a pivotal connection with a thrust rod 62 which in conventional fashion is arranged to be engaged and moved upwardly by suitable cams on the conventional main cam drum of the machine. Upward movement of the push rod 62 effects downward movement of the bushing 54 and with it the gears 44 and 46 against the action of spring 50.

For consistency of description citations may be made of the numbers of teeth of the gearing involved in the drive, though it will be understood that the numbers of teeth may obviously be varied in accordance with the results desired. Gear 44 will be assumed to have 35 teeth and gear 46 will be assumed to have 36 teeth.

The gears 44 and 46 mesh with gear portions of a composite gear 64 journalled on a fixed stud 66. The respective gear portions are indicated at 68 and 70, the former having 36 teeth and meshing with the gear 44, and the latter having 35 teeth and meshing with the gear 46.

The composite gear 64 has bearing on its upper surface a non-rotating friction pad 72 in an assembly which is urged downwardly by a spring 74 the force exerted by which is adjustable. This arrangement imposes some restraint on movement of the composite gear 64 to prevent backlash. This prevention of backlash is important in view of the fact that in a fine gauge machine having, for example, 400 needles in its cylinder, slight relative movement of a train of gearing may produce departure from the accurate alignment of the transfer elements 16 with the needles as is necessary for proper operation during transfers.

An idler 76 is journalled on a fixed stud 78 and meshes with the gear 64. This idler may have 35 teeth. Another idler 80 journalled on the fixed stud 82 meshes with idler 76 and may have 36 teeth. (From the standpoint .of drive ratio, of course, the numbers of teeth on the idlers just mentioned is immaterial; but it is desirable that the numbers of teeth should be different in successive gears through the system to distribute wear.)

A gear 84 having 35 teeth meshes with the idler 80 and is secured to the shaft 32 which is in turn secured to the dial 14.

The housing 34 mounts all of the rotating elements which have been described.

Reference may now be made particularly to FIG- URES 3, 4 and 5. The gear 44 is provided with a hollow portion bounded by a ring from which there inwardly projects a lug 86 engageable by the key projection 40. The gear 46 is of similar construction and has an inwardly projecting lug 88 also engageable by the key projection 40. The drive clutch arrangement thus provided is most clearly illustrated in FIGURE 5, from which it will be evident that when the gears 44 and 46 are in their upper positions the projection 40 will engage the lug 86, while when these gears are in their lower positions the same projection 40 will engage the lug 88.

In the former upper position of the gears, therefore, the .gear 44 having 35 teeth drives the gear 68 having 36 teeth, and through the idlers 76 and 80 having, respectively, 35 and 36 teeth, the gear 84 having 35 teeth. The cylinder and dial are thus driven in a 1:1 ratio. On the other hand, when the gears 44 and 46 are in their lower position, the gear 46 having 36 teeth drives the gear 70 having 35 teeth and gear 68, rotating with gear 70 and having 36 teeth, drives the gear 84 having 35 teeth through the idlers 76 and 80, so that the dial is driven in the ratio 36 /35 or approximately 1.058z1 with respect to the needle cylinder. Thus the dial slowly advances relatively to the needle cylinder.

If, after this slow advance of the dial relative to the needle cylinder is initiated, the gears 44 and 46 are again restored to their upper position under the action of spring 50, the 1:1 drive ratio is restored, but only after the lug 40 reengages the projection 86, the lug 40 making a necessary partial revolution before such reengagement. The result is that the transfer elements are individually returned to association with their needles so that operations are not disturbed. It may be noted that this restoration of a one to one individual relationship between the elements and needles has no fundamental significance with respect to transfer; but it is important to render unnecessary special timing controls involved in the insertion or removal of cams controlling the transfer elements. conventionally, the elements are provided with butts of different lengths so that operating cams may be introduced and removed to provide operational cycles beginning with particular needles, and the restoration of a definite relationship between the dial and cylinder makes this possible without taking into account some arbitrary relative position which would throw the different sets of butts into varying positions with respect to operating cam steps. As will become apparent, in the machine here disclosed the relative creeping movement of the dial relative to the cylinder takes place at a time when the transfer elements are idle. When they are active in the formation of a turned welt, the definite relationship between the dial and cylinder exists and they rotate at the same speed.

The creeping movement of the dial with respect to the cylinder is desirable to insure the production of short ends particularly during splicing, and what is involved will be made clear by particular reference to FIGURES 2, 6 and 7. Referring first to FIGURE 2, when the splicing yarn is taken by the first needle of the splicing panel which rides high by needle selection as previously mentioned, the splicing yarn finger 28 remaining in operation throughout the production of a spliced area, the splicing yarn occupies the position indicates at A in FIGURE 2, extending from the finger 28 about the successive pins 92,, 94 and 98 with its free end drawn into the suction tube 100. As will be seen from this path A, as it is engaged by a needle and then drawn downwardly as the needle descends it will be engaged by a tooth 22 on the annulus which is closely adjacent to but slightly following the first yam-engaging needle. If, then, the annulus and the needles rotated in the same circumferential speed, when the yarn reached the cutter 24 it would be severed closely adjacent to the needle which first engaged it. This has been the usual procedure and has presented no difiiculty.

However, when the yarn is removed, i.e. engaged by the last needle of the splicing panel and missed by the next following needle, a different situation exists. The last needle to engage it is indicated in N in FIGURE 2, and the yarn extends from this needle to the throat plate for finger 28 along a path such as indicated at B. As will be seen, the yarn would then be engaged by a tooth sub stantially lagging the needle N for example the tooth indicated at T If then, the annulus 20 rotated at the same speed as the needle cylinder, the yarn as presented to the cutter 24 would extend in a direction having a considerable horizontal component from the needle N with the result that it would be severed by the cutter 24 at a substantial distance behind the needle N producing a relatively long yarn end.

In accordance with the invention the creep of the dial and with it the annulus 20 will advance the tooth T faster than the needle N so that when the cutter is reached the yarn extends from the needle more nearly vertically and will thus be cut by the cutter 24 close to the needle leaving a short end.

What occurs in accordance with the invention may now be seen by referring to FIGURES 6 and 7. Considering the latter, it will be seen that at the position of the cutter 24 the tooth T engaged by the yarn extending at B from the needle N is in a position not far removed from the needle so that this short cut end is produced. If it were not for the differential speed, the yarn would extend to the tooth located, for example, two or three teeth behind the position illustrated for the tooth T with a considerably greater slope toward the horizontal of the yarn path.

It was remarked that without the slipping advance of the dial the cutting of the yarn when first seized by the needle N would have been satisfactory. But the situation in producing a short yarn end is not adversely effected by the clipping action since, though the tooth T is advanced relatively to the needle N as indicated by the path shown at A in FIGURE 6, the efiect is merely to shift the yarn from a position lagging the needle to a position slightly in advance of the needle to about the same angular distance relative to the vertical through the needle N Thus, substantially the same short end is produced as would be produced if the dial and cylinder rotated at the same speed. In other words, viewing FIGURE 6, the path of the yarn would be from the needle N to a tooth position 3 or 4 teeth behind the one shown at T if the dial and cylinder had rotated at the same speed.

The creeping action which is continued throughout a splicing operation is provided, as already explained, by the shift of the gears 44 and 46 downwardly against the action of spring 5G to bring into operation the gear train 46, 70, 63, 76, 86, 84. After completion of the splicing the gears 44 and 56 are restored to their initial positions to provide the 1:1 drive between the dial and cylinder. This shift back to the normal 1:1 drive may be made at any time following the termination of production of a spliced area so long as it does occur before the next formation of a turned welt. During the formation of a turned welt, of course, since the transfer elements will be active, the 1:1

' drive ratio is desired with each element located above a particular needle. Timing, of course, is taken into account to prevent any jamming of the lug 40 with respect to the inward projections 86 and 88.

While the action just described is particularly advantageous for the production of short ends during splicing, in which case long yarn ends would be more noticeable, it will be evident that the same operations may be used in securing short yarn ends when yarn changes are produced since when a yarn is taken out of action there will be produced a long clipped end in accordance with the prior type of operation whereas a shorter end will be produced if the creeping action takes place as described. In the case of yarn changing the enclosing yarn will be clipped as close to the needles as in the prior type of operation in view of the slight shift of the slope of the yarn from a position lagging the needle to one preceding the needle by which it is first engaged.

It will be evident that various other uses may be made of the creeping movement of the dial relative to the cylinder, and that various details of construction and operation may be changed without departing from the invention as defined in the following claims.

What is claimed is:

1. A knitting machine comprising a pair of coaxial rotary beds at least one of which carries independent needles while the other carries elements adapted to cooperate with the needles for the formation of knitted fabric, and driving means connecting said beds and arranged to provide selectively a pair of continuous definite but different drive ratios between said beds.

2. A knitting machine according to claim 1 in which one of the drive ratios is 1:1.

3. A knitting machine according to claim 1 in which one of the drive ratios is 1:1 and in which the other of said drive ratios differs slightly from 1:1 to provide a relative creeping movement between the beds.

4. A knitting machine according to claim 1 in which the first mentioned bed is a needle cylinder and said other bed is a dial.

5. A knitting machine according to claim 4 in which one of the drive ratios is 1:1.

6. A knitting machine according to claim 1 in which the first mentioned bed is a needle cylinder and said other bed is a dial carrying transfer elements for the production of turned welts.

7. A knitting machine according one of the drive ratios is 1:1.

8. A knitting machine according to claim 1 in which said driving means includes a pair of selective gear trains.

9. A knitting machine comprising a needle cylinder,

to claim 6 in which independent needles carried by said cylinder, elements cooperating with said needles for the formation of stitches including yarn feeding means, means for rotating said cylinder, yarn cutting means adjacent to the path of the needles and angularly remote from the yarn feeding means about the axis of the cylinder, means engaging a yarn undergoing a feed change in the vicinity of said feeding means to carry it to said cutting means for severance, and means imparting to said engaging means a rotary movement slightly different from, but in fixed ratio to, the rotary movement of said cylinder, said yarn engaging means moving both closely adjacent to the needles and in their direction of rotary movement at the location of said cutting means.

10. A knitting machine according to claim 9 in which said engaging means is in the form of an element having radially outwardly extending members and mounted for rotation at least approximately coaxial with said cylinder.

11. A knitting machine according to claim 9 in which said engaging means is a toothed annular element mounted for rotation at least approximately coaxial with said cylinder.

12. A knitting machine according to claim 9 in which the rotary movement imparted to said engaging means is slightly greater than the rotary movement of the cylinder.

13. A knitting machine according to claim 9 in which yarn is taken only by a selected panel of needles in each of a series of consecutive rotations of the needle cylinder.

14. A knitting machine according to claim 9 in which said engaging means engages a yarn as it is disengaged by needles and becomes inactive.

15. A knitting machine according to claim 9 in which said engaging means engages a yarn as it is engaged by needles and becomes active.

16. A knitting machine according to claim 9 in which said engaging means engages a yarn as it is disengaged by needles and becomes inactive, and also as it is engaged by needles and becomes active.

17. A knitting machine comprising a needle cylinder, independent needles carried by said cylinder, elements cooperating with said needles for the formation of stitches including yarn feeding means, means for rotating said cylinder, yarn cutting means adjacent to the path of the needles and angularly remote from the yarn feeding means about the axis of the cylinder, a dial mounted coaxially with said cylinder, transfer elements mounted in said dial, means providing teeth rotatable with said dial for engaging a yarn undergoing a feed change in the vicinity of said feeding means to carry it to said cutting means, and mean selectively operable to drive said dial either at the speed of said cylinder or at a speed slightly different from that of said cylinder.

18. A knitting machine comprising a needle cylinder, independent needles carried by said cylinder, elements cooperating with said needles for the formation of stitches including yarn feeding means, means for rotating said cylinder, yarn cutting means adjacent to the path of the needles and angularly remote from the yarn feeding means about the axis of the cylinder, a dial mounted coaxially with said cylinder, transfer element mounted in said dial, means providing teeth rotatable With said dial for engaging a yarn undergoing a feed change in the vicinity of said feeding means to carry it to said cutting means, and means selectively operable to drive said dial either at the speed of said cylinder or at a speed slightly greater than that of said cylinder.

19. A knitting machine according to claim 18 in which said engaging means engages a yarn as it is disengaged by needles and becomes inactive.

20. A knitting machine according to claim 18 in which said engaging means engages a yarn as it is disengaged by needles and becomes inactive and also as it is engaged by needles and becomes active.

References Cited by the Examiner UNITED STATES PATENTS 1,817,566 8/1931 Jones 6626 1,945,971 2/ 1934 Gagne 66145 1,998,473 4/ 1935 Welch et al 668 3,081,609 3/1963 Mahler 66134 3,164,975 1/ 1965 Haberhauer 66145 3,197,977 8/1965 Stack 66134 X 3,252,307 5/1966 Kaese 66134 3,257,829 6/1966 Parthum 66-134 FOREIGN PATENTS 685,501 4/1964 Canada. 1,323,130 1/1963 France.

MERVIN STEIN, Primary Examiner.

W. C. REYNOLDS, Examiner. 

1. A KNITTING MACHINE COMPRISING A PAIR OF COAXIAL ROTARY BEDS AT LEAST ONE OF WHICH CARRIES INDEPENDENT NEEDLES WHILE THE OTHER CARRIES ELEMENT ADAPTED TO COOPERATE WITH THE NEEDLES FOR THE FORMATION OF KNITTED FABRIC, AND DRIVING MEANS CONNECTING SAID BEDS AND ARRANGED TO PROVIDE SELECTIVELY A PAIR OF CONTINUOUS DEFINITE BUT DIFFERENT DRIVE RATIOS BETWEEN SAID BEDS. 